Fluid vortex transducer



1968 R. E. BOWLES ET AL 3,

FLUID VORTEX TRANSDUCER Original Filed Aug. 11. 1960 3 Sheets-Sheet 1grwmvtoq/L RONALD 5..BOU)LES 56 B\LLY M. HORTON Dec. 24, 1968 R. E.BOWLES ET AL 3,417,624

FLUID VORTEX TRANSDUCER Original Filed Aug. 11. 1960 5 Sheets-Sheet 2 iia! so 5! I awe/whom. Romm E .Bomus a- Buux M. Hon-con Dec. 24, 1968 R.E. BOWLES ET AL 3,417,624

FLUID VORTEX TRANSDUCER Original Filed Aug. 11, 1960 3 Sheets-Sheet 5lGal go RONALD E.BOUJLES & BILLY M.HQRTN United States Patent 16 Claims.(Cl. 73432) ABSTRACT OF THE DISCLOSURE The invention provides a vortexchamber into which fluid is introduced radially so as to flow to anegress orifice coaxial with the chamber. A rotary device is locateddownstream of the egress orifice so as to rotate in a sense and at avelocity determined by the sense and rate of rotation of fluid in theegress orifice. The rate and sense of rotation of the device isconverted to an electrical signal by a generator driven by the rotarydevice.

This application is a division of U.S. application Ser. No. 439,500,filed Feb. 23, 1965, in the names of Romald E. Bowles and Billy M.Horton and entitled, Fluid Amplifier, now Patent No. 3,276,259 which wasa continuation of U.S. application Ser. No. 49,061 filed Aug. 11, 1960,now abandoned.

This invention relates to fluid vortex amplifiers, which utilize theflow of fluid, fluid characteristics, and fluid flow characteristics toamplify an input signal. In general, the vortex amplifier of the presentinvention does not require moving mechanical parts other than the movingfluid itself. This is advantageous in that the use of moving mechanicalparts limits the accuracy, reliability and utility of fluid systems toextents which vary with the particular application, because of friction,thermal expansion or deterioration, production tolerances, assemblyproblems, inertia or weight, response times, etc., of the moving parts.Consequently, elimination or reduction of the number of mechanicallymoving parts is advantageous from the viewpoint of improvingreliability, ruggedness, storage life, initial cost, and simplificatonof the system.

This invention utilizes rotational flow, irrotational flow, fluid flowdistribtuion, transport characteristics, boundary layer effects,pressure distribution, vanes, deflectors, surface characteristics, fluidproperties, hydrostatics and fluid dynamics to achieve its objectives.The device can be considered an amplifier because the energy controlledis larger than the controlling energy. The fluid employed can be liquid,gaseous, mixtures of fluids, or combination wherein different fluids areused in diiferent sections of the fluid vortex amplifier.

Consider a circular pan of liquid provided with a small discharge holeat the bottom center. The height of liquid in the pan results in ahydrostatic head or pressure which ends to force the fluid out of thesmall centrally located discharge hole. In the case of irrotational flowthe fluid will flow radially towards and through the discharge hole. Foran incompressible fluid the flow velocity will be inversely related tothe liquid radial location. If one considers a two dimensionalirrotational flow condition, as in the case of flow to a simple sink,the radial velocity V and the radial position r will be related as inEquation 1 constant If the fluid is compressible then the local fluiddensity p must be considered and Equation 1 becomes eonstant If atangential component of velocity is imparted to the fluid immediatelyadjacent to the pan rim, a fluid annulus rotates as a whole about thedischarge hole as an axis, and the flow is now rotational rather thanirrotational. It has been shown mathematically in numerous text booksthat as this annulus shrinks towards the centrally located outlet, thetangential velocity component V, for simple rotational flow is relatedto the radial position by Equation 3.

constant Consequently, when the fluid is discharging from the pan, asfluid moves from the rim towards the centrally located discharge holeits tangential velocity component V, increases as the radial positiondecreases. Ideally it one start with a 10" diameter pan dischargingthrough a centrally located hole of .01 diameter the tangential velocitycomponent at the discharge hole V would be one thousand times thetangential velocity component at the rim of the pan V Thus thetangential velocity component is amplified.

While an open pan of liquid has been used to describe in elementaryfashion the operation of a vortex amplifier, preferred embodiments ofthe invention employ a closed container or vortex chamber, wherein thefluid need not be liquid but can be a liquid or'a gas or a mixture offluid or combinations of fiuids and where the source of pressure causingfluid discharge need not be derived from gravitational elfects but canbe due to an initial pressurization of the vortex chamber, or to elasticdeformation of the vortex chamber, or to generation of fluid pressure byaddition of energy to the fluid vortex chamber, or to a replenshing flowof fluid or fluids into the vortex chamber at a radius different fromthe discharge radius.

It is, accordingly, a broad object of the present invention to provide afluid vortex amplifier.

It is another object of the invention to provide a fluid vortexamplifier having provision for plural inputs at different radialdistances from an output port.

It is a further object of the invention to provide systems for measuringrotary velocity of fluid flow from a vortex amplifier output port.

Still another object of the present invention is to provide a system forbiasing a vortex amplifier.

A further object of the invention resides in the provision of adifferential vortex amplifier.

Another object of the invention is to provide a vortex amplifier havinga multiplicity of inputs at different radii.

A further object of the invention is to provide a device for measuringboth the sense and magnitude of rotation of fluid flowing from theoutput port of a fluid amplifier.

The above and still further objects, features and advantages of thepresent invention will become apparent upon consideration of thefollowing detailed description of one specific embodiment thereof,especially when taken in conjunction with the accompanying drawings,wherein:

FIGURE 1 is a view in plan of a first embodiment of the vortex fluidamplifier of the present invention;

FIGURE 2 is a view in section, taken on the line 22 of FIGURE 1;

FIGURE 3 is a view in plan of a modification of the system of FIGURE 1;

FIGURE 4 is a view in section, taken on the line 4-4 of FIGURE 3;

FIGURE is a view in plan of a differential fluid vortex amplifier,according to the invention;

FIGURE 6 is a view in section, taken on line 6-6 of FIGURE 5;

FIGURE 7 is a view in plan of a multiple input fluid vortex amplifier;and

FIGURE -8 is a view in section taken on the line 8--8 of FIGURE 7.

Referring now more particularly to FIGURES 1 and 2 of the accompanyingdrawings, the reference numeral CL refers to the center line, or thecenter of axial symmetry, of a vortex chamber 1. The vortex chamber 1 isa generally closed cylindrical structure having a base 2, a top wall 3and a cylindrical wall 4 joining the base 2 and the top wall 3. Anegress discharge or output port or opening 5 is provided in the base 2and is located symmetrically of the latter, being centered on the centerline CL of the vortex chamber 1.

Distributed about the top wall 3 are input openings 6, the distributionbeing equi-angular and at approximately the maximum radius availablewithin the vortex chamher 1. Communicating with the openings 6 aresupply lines 7 in the form of tubes terminating at the openings 6 andeach extending perpendicularly of the top wall 3. The tubes 7 supplyfluid to the vortex chamber 1 via the openings 6 which are arranged tobe perpendicular with respect to the top wall 3 so that they willintroduce no relative tangential velocity component of fluid flow. Theprecise number of tubes 7 which is utilized in any specific embodimentof the invention represent a matter of engineering choice, but aconsiderable number is desirable in order that random relativetangential flow of fluid may be avoided. In the specific embodimentillustrated 24 such tubes are provided. The tubes 7 are supplied withfluid by means of manifolds 8, all of which communicate with a mainsupply line or conduit 9. An alternative conduit 10 supplies fluid tostill a further supply line 11 located at a different radius than arethe supply lines 7. Fluid is supplied to the main supply lines 9 and 10via a proportioning valve 12 from a tube 13, which is connected to asource of fluid under pressure, such as a pump or other convenientdevice (not shown). The proportioning valve 12 permits of controllingthe proportion of fluid provided via tube 13 to the manifolds 9 and 10,and accordingly permits control of relative fluid flow through thesupply lines 7 and 11, respectively. These, being at different radii,respectively, induce different velocities of fluid flow at the centerline CL, or at the outlet port 5, and the resultant rotary velocity offluid at the outlet port 5, in response to any tangential flow inducedin the chamber 1, by any means, is accordingly controllable bymanipulation of the proportioning valve 12.

So long as no tangential or rotary component of fluid flow is introducedinto the vortex chamber 1 the flow will be radial toward the outlet port5. Any tangential component of flow within the chamber 1, which may beintroduced in any manner whatsoever, at a radius within the chamber 1which is greater than the radius of the outlet port 5, will cause anamplified rotary flow at the outlet port 5, i.e. the flow at the port 5will rotate more rapidly than does the flow at any point within thechamber having a greater radius than does port 5.

The output port 5 is connected to a pipe 15 within which is located apaddle wheel consisting of flat planes which intercept on a linecoincident with CL. The paddle wheel 16 is mechanically coupled to asmall D.C. generator 17, which has a voltage output depending upon speedand sense of rotation, but which requires essentially negligible powerfor driving purposes. The generator 17 is connected to an indicator 18,which may be a voltmeter, and which accordingly is capable of beingcalibrated in terms of the rotary velocity of the paddle 16, to indicateboth sense and magnitude thereof. The paddle 16 is stationary so long asthe flow of fluid through the port 5 is radial, i.e. contains 119 gt rycomponent,

and the voltmeter 18 accordingly reads zero. When however a rotarycomponent exists the paddle wheel 16 is rotated thereby, and drives thegenerator 17 at a proportional or equal velocity, and the latterprovides a voltage to the voltmeter 18 which can be read against a scalecalibrated in terms of rotary velocity, and having a polarity determinedby sense of rotation.

Reviewing now the operation of the system of FIG- URES 1 and 2, anddescribing same in mathematical terms, in FIGURES l and 2, the vortexchamber 1 is substantially a circular cylinder provided with a dischargeorifice or port 5, located at the cylinders longitudinal axis CL. Thedischarge fluid stream will rotate about the vortex chamber axis CL witha tangential velocity component governed by Equation 3 and by anytangential velocity component introduced into the vortex chamber fluid.If this tangential velocity component is introduced as the fluid entersthe chamber as V or initial tangential velocity component, then thecondition at discharge V is given by Equation 4 (4) va n.

Where r and r are the radial locations of the inlet and discharge withrespect to the centerline CL and where 1 is a nonlinear modificationintroduced by viscous forces and is equal to one in the absence ofviscosity.

Pressurized fluid is supplied by proportioning valve 12 to distributionmanifolds 9 and 10 and thence to paths 7 and 11. The openings 6 and theexit of path 11 are so oriented and shaped that they do not provide arelative flow velocity component which rotates about the vortex chamberlongitudinal axis CL. The manifold 8 and paths 7 are shaped andconnected so as to avoid introducing an initial relative rotational flowwhen fluid enters the vortex chamber 1. We may now assume thattangential components of velocity are imparted to the fluid, in anydesired fashion. If r is the radial location of the distribution paths 7and if r is the radial location of the fluid discharging from the vortexchamber 1 then the tangential velocity components V and V at radius rand r respectively are related as in Equation 5 where 1 is amodification introduced by viscous forces Consider a condition whereinthe fluid in the vortex chamber at its outermost radius is rotating at aconstant angular rate In order to develop a useful output signal fromthe apparatus means must be provided for monitoring the tangentialvelocity component at the discharge V One extremely simple monitoringmethod is to place a paddle wheel 16 in the discharge stream with thepaddle wheel axis of rotation coincident with and parallel with thevortex chamber axis CL and with paddle wheel blades which are flatplanes passing through the paddlewheel axis of rotation. Then theangular rotation rate of the paddle wheel, W will be related to thedischarge tangential velocity component V by Equation 8 K issubstantially a constant and is approximately equal to unity.

If the valve 12 which supplies fluid to the vortex amplifier directs allof the fluid to distribution paths 7, then And because the values 1' andr are fixed and the values K and n are approximately constant then it lK then let and

(13) W AW K In FIGURE 1, r r such that A 1 and the amplitude of W W Itis apparent to one skilled in the art that the discharge can be throughan annular ring and a model can be constructed wherein r is less than rsuch that A 1.

If the valve 12 which supplies fluid to the vortex amplifler directs allof the fluid to distribution path 11 then one finds that, by analogywith Equation 11, W depends upon the inlet radial position r thedischarge radial position r the monitor coeflicient K, the viscositymodification within the vortex chamber 1 and the angular rate ofrotation of the fluid at radius r W Thus, one is able to employ theembodiment of FIG- URE 1 as a multiplier and by controlling the radiallocation at which fluid is introduced, one is able to change themultiplication coefiicient, as illustrated above, from value A to valueB, or, similarly, to any other fixed value.

It is also possible to proportionally supply fluid to inlets ordistribution paths at several radial locations simultaneously. In suchcases the momentum exchange between fluid introduced at a large radiallocation r and fluid introduced at a smaller radial location r must beconsidered.

Let i22 indicate the mass flow rate of fluid introduced at r and let mindicate the mass flow rate of fluid introduced at 1' By the time itgets to location r the mass m has a radial velocity component based onEquation 2 and conservation of mass as follows 16 m= VA Wherein pm5,5 isdensity of m at position r V is radial velocity at 2' h is height ofvortex chamber A is radial flow area 21rrh r5 pm5 527l'1'5h At positionr a radial location slightly greater than r The tangential fluidvelocity of #1 at "6+9 is The velocity of tit at locations r +e istherefore 21 (s+z)=\ i ,f|-

The tangential momentum component of m at r +e is The tangentialvelocity of m at r is (25) V WI, The tangential momentum of m r (26) P=7hsT W The combined tangential momentum at r e is t t t 2 8) 1 s l1 5mm) The tangential velocity component of the combined flow is Based onEquations 4 and 30 the discharge tangential velocity component V isWherein 7 represents the viscous force modification of the idealizedflow between radial locations r and r and Wherein 1 represents theviscous force modification of the idealized flow between radiallocations r and r Comparison with Equations 13 and 15 is instructive.

It is apparent that a similar analysis can be readily accomplished whenfluid is introduced at more than two radial locations. It is alsoapparent that discharge can be at more than one radial location ifdesired, as a means of reducing the number of units required in asystem.

Referring now more particularly to FIGURES 3 and 4 of the accompanyingdrawings, CL again represents the center line of a chamber 21 having abase 22 and a top wall 23 joined by a cylindrical wall 24, forming asubstantially closed hollow cylindrical enclosure. Pressurized fluid issupplied to the chamber 21 via a radially extending pipe 25, terminatingat cylindrical wall 24. Located within the chamber 21 is a furtherchamber 26 comprised of a disc like top wall 27 extending parallel withand slightly spaced from top wall 23, and an annular or cylindrical wall28 extending parallel to and within the wall 24 of the chamber 21. Thelower annular edge or rim of the annular member 28 rides within anannular groove 29 in the inward surface of the base 22 of the chamber21. The annular ring 28 and its closure disc 27 are driven by means of amotor M, mechanically coupled to the center line of the top wall 27. Themotor M is driven at variable speeds from a source of voltage 30, via avoltage or speed regulator 31. Fluid supplied through the pipe 25 entersthe annular chamber existing between the cylindrical walls 24 and 28 byvirtue of the spacing therebetween, and provides a fluid pressure headtherein. Communication through the annular wall 28, from the annulardistribution chamber 21 formed by walls 24, 25 and the cylindricalvortex chamber 26 located interiorly of annular wall 28 is provided bymeans of slots 32 and 33, which make a common angle with respect to, buton opposite sides of, the diameter joining the outlets 34, of the slotsso that fluid entering the inner chamber via the slots 32, 33 isprovided with a tangential component of velocity. Since the angles whichthe slots 32, 33 make with the diameter are equal, and since the egresspoints of the slots 32, 33 fall on the diameter D of chamber 26, arotary couple is provided which is symmetrical with the respect to thecenter line CL.

Located in the base 22 and symmetrical with CL is an outlet ordischarged orifice 35. The latter extends into a cylindrical enclosure36, which extends downwardly of base 22. A series of annular receivingapertures 37 is provided, which extend into the enclosure 36 and whichface generally the discharge orifice 35. As illustrated in theaccompanying drawings, the receiving annular receiving apertures includeone aperture 38 which is aligned with the discharge aperture 35, andfurther apertures 39, 40, 41 and 42, which are successively of greaterdiameters, and which surround the central aperture 38 and aresymmetrical therewith. Each of the annular receiving apertures 38, 39,40, 41 and 42 communicates via a suitable line, as 43, with a pressureactuated diaphragm type pressure indicator, as 44.

In the systems of FIGURES 3 and 4, fluid supplied via pipe 25 to theannular chamber between walls 24 and 28 flows through the slots 32 and33 into the vortex chamber. The slots 32 and 33 are so arranged thatfluid entering the vortex chamber has a tangential velocity componentdue to the speed of flow in slots 32 and 33, which would exist even ifthe latter were stationary. An additional component of tangentialvelocity can be produced by rotating the annular wall 28 and thereby theslots 32 and 33. This rotation is accomplished in response to therotation of the motor M, and can be in either sense of rotation, bymaking the motor M reversible. Assuming that annulus 28 is rotating, thelatter acts as a torsional inertia with regards to flow from the annularchamber to vortex chamber 21. Because slots 32 and 33 are not radial theflow exists from these slots with a velocity which is not radial andconsequently a force acts on the walls of flow paths or slots 32 and 33,tending to cause the member 28 to rotate or increase its rate ofrotation about the center line CL. The rate of rotation of member 28will increase until the fluid exit via 35 has the same velocity vectordirection as the entrance velocity vector direction for the same flowpath. Thus if the main body has a rotational rate W which is negligible,then the transient tangential velocity component Vtq at radius.

r-; (the exit radius of flow paths 32, 33), which results from theaction of flow through paths 32, 33 in member 28 is amplified to alarger tangential velocity component at the discharge radius r by flowthrough the vortex chamber.

(40) m tan or 1 t 27m}! +21rr W when 111 is the volume flow rate of thesystem and tan a is negative for orientation of flow paths 22 as shownin FIGURE 3. Let 1 equal the angular moment of inertia of member 28.Then the transient is identified by the following It is apparent that asimilar effect occurs if m, is decreased in that the angular momentum ofmember 28 introduces a signal Vt' on the reduced flow m. If the reducedvalue of m, is zero then there is no flow to discharge path 35 andexcept as attentuated by friction and viscous action the angularmomentum of member 28 is stored until flow m resumes.

In some applications it is desirable to rotate member 28 through asuitable mechanical linkage in order to introduced a value of V which isrelated to an input signal. Unless otherwise specified the term inputsignal as used herein is a fluid signal which is intentionally suppliedto the system for the purpose of instructing or commanding the system toprovide a desired output signal. This input: signal can be in the formof time or spatial variations in pressure, density, flow velocity, massflow rate, fluid composition, transport properties, or otherthermodynamic properties of the input fluid. The term output signal asused herein is a fluid signal which is provided by the system at itsoutput. This output signal can be in the form of time or spatialvariation in pressure, density, flow velocity, mass flow rate, fluidcomposition, transport properties, or other thermodynamic properties ofthe output fluid.

The rate at which fluid is rotating in proceeding from the outlet port35 determines the solid angle of spread which the fluid will make afterleaving the port 35. If the fluid is not rotating, all the fluid, orsubstantially all the fluid, Will be directed to the central receivingaperture 38. The more rapidly the fluid is rotating the greater will bethe distribution over the angular receiving ports 39 to 42. Accordinglyvisual observation of the measuring devices 44 will result in indicationof the rotation of the fluid emitted from port 35.

If now a component of rotation of fluid within the vortex chamber isproduced, in response to any type of input signal, this component can bebalanced by appropriate rotation of the annular wall 28, and if therequired speed of rotation of the motor M to effect balance 9 is known,the magnitude of the input signal may also be know.

In the alternative the system may be utilized to measure the rate ofrotation of the motor M, in terms of the solid angle provided by therotating fluid emitted from the port 35, as these are indicated by thepressure measuring or indicating device 44.

In the system of FIGURES and 6 a cylindrical chamber 50 is providedhaving a base 51 and a top wall 52 joined by a cylindrical wall 53 toform a closed hollow cylindrical enclosure. Within the enclosure isprovided a porous cylindrical wall 55 spaced from the outer wall 53, andextending between the base 51 and the top wall 52, thereby forming anannular passageway 56 between the outer surface of wall 55 and the innersurface of wall 53. Pressure is supplied to the annular passageway 56via a pipe 57, to which is connected a source of fluid under suitablepressure (not shown). The porous wall 55 permits fluid to flow into thechamber formed interiorly of the wall 55, but introduces suflicientresistance to flow of fluid that the entrance of fluid into the chamberformed by the wall 55, and hereinafter called the vortex chamber, has notangential component of velocity but does have a homogeneous radialcomponent of velocity. Outlet ports 60 and 61 are provided in the base51 and in the top wall 52 respectively, the outlet ports being circularand symmetrical with respect to CL, the center line of the vortexchamber. Extending between the ports 60, 61 is an Archimedes screw 63,which forms a helical deflector presenting differential impedance to theflow of fluid which is proceeding through the ports 60 and 61 withrotary component of motion. So long as the rotary component of motioncorresponds in sense with the threads of Archimedes screw 63 the latterfacilitates flow of fluid.

When the fluid is in the opposite sense of rotation, however, theArchimedes screw 63 impedes the flow of fluid. It follows that thequantity of fluid per second which passes through the ports 60 and 61respectively, depends upon the direction in which the fluid is rotatingwithin the vortex chamber. Assuming that the Archimedes screw to have aclockwise direction of thread advance in proceeding from port 60 to port61, then if the flow is clockwise flow is facilitated in passing throughthe port 61, and impeded in passing through the port 60. On the otherhand if the direction of rotation of flow is reversed, i.e. if theArchimedes screw has a direction of advance in proceeding from port 60to 61 which is right-handed or clockwise, the flow is left handed asseen in proceeding from the port 60 to 61, the Archimedes screwfacilities flow through the port 60 but impedes flow through the port61. The port 60 is connected via a channel 65 to an elastic bellows 66having an overflow provision via a small restrictive passage 67.Likewise the port 61 is connected via a channel 68 to a bellows 69,having a restriction overflowing passage 69'. Bellows 66 and 69 arejoined by a connecting rod 70 so that one bellows acts against theother, and the connecting rod 70 is provided with a pointer 71 movingover a scale 72, so that by observation of the position of the pointer71 with respect to the scale 72 one may determine the relativeexpansions of the bellows 66 and 69. The position of the pointer 71,accordingly, establishes a measure of the sense of rotation and velocityof rotation of fluid within the vortex chamber.

Assuming that the Archimedes screw 63 is right-handed in proceeding fromport 60 to port 61, and that rotary flow of fluid within the vortexchamber is right-handed, fluid flow through the port 61 and the channel68 will be greater than is fluid flow through the port 60 and thechannel 65, and accordingly bellow 69 will be under greater pressurethan is bellows 66. Bellow 69 will then overcome bellow 66 and movepointer 71 downwardly to an extent which is a measure of the rotaryvelocity of the fluid in the vortex chamber. If the flow of the fluid inthe vortex chamber is entirely radial, i.e., contains no tangential orrotary component of motion, the Archimedes screw 63 will be neutral andequal flows will occur through the ports 60 and 61 to the bellows 66 and69. In such case the restrictive overflow passages 67 and 69' willprovide equal overflows, and the bellows will provide forces against therods which are equal and opposite. The pointer 71 will then maintain azero deflection.

Exteriorly of the chamber 50 are provided two tubes and 76 in whichoccur fluid flows in the directions of the arrows 77 and 78,respectively. Pitot pressure tube 80 faces upstream in the tube 75 andsimilarly a Pitot pressure tube 81 faces upstream in the tube 76. Fluidcollected by the Pitot pressure tube 80 is supplied to a divider 83,which supplies this fluid to a pair of channels 84 and 85 in equalamounts, channels 84 and 85 terminating in openings in the wall 55 theopenings existing at opposite ends of a diameter, being identifiable bythe reference numerals and 91, and being so oriented with respect to thewall 55 as to introduce equal tangential components of fluid flow.Accordingly there is introduced into the vortex chamber a tangentialcomponent of fluid motion which has a magnitude representative of thepressure measured by the Pitot tube 80.

Similarly, the Pitot tube 81 is connected via a divider 92 to a pair ofchannels 93 and 94, introducing equal flows into these channels, and thechannels 93 and 94 terminate in openings 95 and 96 respectively in thewall 55 of the vortex chamber. The channels 93 and 94, as they enter thewall 55, make a tangential angle with respect thereto, so as tointroduce a tangential flow, and since the ingress points exist alongthe opposite ends of a diameter, a moment of rotation is introducedwhich is symmetrical about the center line CL. The sense of rotationintroduced by the input nozzles 95 and 96 are opposite to thoseintroduced by the input nozzles 90 and 91.

It follows that rotation of the vortex which is induced by the two setsof nozzles 90, 91 and 95, 96, respectively, are subtractive, and the netrotation of fluid in the vortex chamber is thus a measure of thedifference in pressures and flows in the pipes or channel 75, 76 asmeasured by thes Pitot tubes 80, 81.

Provision is made for inserting into the vortex chamber two distinctkinds of impedances to fluid flow. One of these impedances takes theform of cylindrical rods 100 which may be inserted to varying depthsinto the vortex chamber and in a direction parallel to the center lineCL of the chamber. By virtue of the fact that the rods are transverselycylindrical, and of the fact they are located at a smaller radius thanthe radius of injection of fluid with tangential component of flow byinjection nozzles 90, 91 and 95, 96, the rods 100 introduce an impedanceto radial flow which is the same for both directions of rotation. Therods 100 are arrange-d on a common diameter, so as to introduce abalanced impedance couple, and to avoid turbulence, and are mounted on acommon mounting plate 101. Secured to mounting plate 101 is a rack 102,the latter being driven by a pinion 103 in response to rotation of amotor 104. By suitably energizing motor 104 the pinion 103 may berotated and thereby drive the rack 102 vertically, concomitantlyinserting the impedance rods 100 more or less into the vortex chamber,and introducing greater or smaller impedance of fluid flow in thevortex.

A second type of impedance device is provided, which is sensitive todirection of rotation of the fluid within the vortex chamber. Thisimpedance consist of pair of rods 110, 111, mounted on a common diameteron opposite sides of the center line CL of the vortex, and at equalradii. In cross section, the rods and 111 are semicircular, the convexsurfaces of the rods 110, 111 facing in the same sense the clockwiserotation of the fluid, but presenting a relatively small resistance tosuch clockwise rotation because of the aerodynamic shape of the rods.

On the other hand, in response to counter-clockwise rotation, the rods110, 111 are concave as seen by the fluid, and accordingly relativelyhigh impedance to flow is introduced. As in the case of the rods 100,the rods 110 and 111 are mounted on a transverse plate 112, which servesto support both rods 110 and 111, and which is secured to a rack 113which is driven by means of a pinion 114 in response to rotation of thedrive motor 115.

The rods 100 can be used to symmetrically (while rods 110, 111 can beutilized to unsymmetrically) reduce rate of rotation within the vortexchamber of the fluid within the vortex chamber, and consequently toreduce the maximum deflection of the pointer 71, in effect reducing thetotal scale of magnitudes of pressures supplied to the bellows 66 and 69to a relatively small range of values, while the pressures and flows inthe tubes 75 and 76 may vary over a great range of values.

In the systems of FIGURES 7 and 8 we employ a vortex structure involvingan outer cylindrical container having a bottom wall 120 and a paralleltop wall 121, joined by a cylindrical wall 122 to form a substantiallycomplete cylindrical hollow enclosure. Within the enclosure is a porouscylindrical wall 123 which extends between the base 120 and the top wall121, but is spaced from the cylindrical wall 122 so as to form a channel123' of annular shape, which may be utilized to supply fluid underpressure to the interior of a vortex chamber 124, formed by the interiorsurface of the wall 123, the base 120 and the top wall 121.

Fluid is supplied to the annular passage 123 by means of a pipe 125, andpasses through the porous wall 123, entering into the vortex chamber 124radially and with no component of relative tangential or rotary motion.A pipe 130 is provided, having therein fluid flow in a directionindicated by the arrow 131. A pressure monitor tube 132 extends throughthe wall of the tube 130 at right angles therewith, and accordinglytransmits a pressure equal to the static pressure in the tube 130. APitot tube 133 is provided, with faces upstream in the conduit 130, andaccordingly measures the total pressure therein. Flow in the pipe 132,representative of static pressure in the channel 130, divided equally bymeans of a divider 135 into two channels 136 and 137. The latterchannels terminate on a common diameter of the vortex chamber 124, andat equal distances from the center line CL thereof. The nozzles of thechannels 136 and 137 are directed in opposite senses, so as to effectrotation of fluid within the vortex chamber 124 in the same sense, i.e.counterclockwise as seen in FIGURE 7.

The output of Pitot tube 133 is applied to a divider 140, which dividesthe output of the Pitot tube 133 equally and applies the two equalportions in separate channels 141 and 142, which terminate in nozzles143 and 144 respectively, located on a common diameter of the vortexchamber 124 at equal distances from the center line CL. The nozzles 143and 144 inject fluid into the vortex cham her 124 in such sense as tocause clockwise rotation of fluid therein.

A source of fluid pressure 150 is provided, which is valved by means ofa valve 151 and measured in respect to amplitude by means of a meter153. The fluid passed by the valve 151 is divided in a divider 154, andequally divided fluid flows supplied via conduits 155 and 156,respectively, to nozzles 157 and 158, which tend to cause clockwiserotation of the fluid in the vortex chamber 124, by reason of theirorientations and by the fact that they are at equal distances along acommon diameter of the vortex. A further source of fluid under pressure,160, is valved by means of a valve 161 and its pressure monitored bymeans of a meter 162. The fluid passed by the valve 161 is divided in adivider 163 into equal flows, which proceed via conduits 164 and 165respectively to nozzles 167, 168 located on a common diameter onopposite sides of center line CL. The distance between nozzles 167 and168 can be the same as the distance between nozzles 157 and 158,

deriving from valve 151. On the other hand the distance between nozzlesderiving from the Pitot tube 133 and from the static pressure tube 132can be at equal distance separations. The Pitot tube pressure causesclockwise rotation of the fluid and the static pressure causescounterclockwise rotation. These rotations can be counter-balanced byfluid injected from the valves 151 and 161, whereof the fluid injectedfrom the valve 151 causes clockwise rotation and that from the valve 161counterclockwise rotation.

The total rotation within the vortex chamber 124 can be measured as inthe system of FIGURES 5 and 6, if desired. However, in accordance withthe embodiment of our invention illustrated in FIGURES 7 and 8, thescrew of FIGURES 5 and 6 is dispensed with, and instead we utilize apair of vertical channels or outlet ports, 170, 171, located in symmetrywith center line CL, and each containing at its opening a scoop arrangedto accept fluid flowing in a first direction and to reject fluid flowingin an opposite direction. The outlet or egress ports communicate withbellows as in the case of FIGURES 5 and 6, and accordingly this portionof the structure requires no further elucidation.

The system of FIGURES 7 and 8 operates to measure either total pressuresor static pressures, or the difference between these, by supplyingcountervaling biases from the valves 151 and 161. These valves may beadjusted so as to reduce the total rotation within the vortex chamber tozero, whereupon a reading of the pressures provided by meters 153 or 162on both of them enables a deduction as to the chamber of them ormagnitude of the pressures in the channel 130.

While we have described and illustrated several specific embodiments ofour invention, it will be clear that variations of the details ofconstruction which are specifically illustrated and described may beresorted to without departing from the true spirit and scope of theinvention as defined in the appended claims.

What we claim is:

1. In combination, a vortex chamber having a means for supplying fluidwith substantially no tangential velocity relative to said chamber at alocation having a large radial displacement from an axis of saidchamber, said chamber also having an outlet aperture for fluid, saidaperture being located adjacent said axis and having a radial lengthsmall relative to the aforesaid radial displacement, fluid in saidchamber being responsive to external motivation to produce rotationalvelocity of said fluid about said axis, a rotatable member locatedwholly downstream of said aperture and in fluid flow communicationtherewith, and means for determining the rate of rotation of saidrotatable member.

2. In combination, a vortex chamber having a means for supplying fluidwith substantially no tangential velocity relative to said chamber at alocation having a large radial displacement from an axis of saidchamber, said chamber also having an outlet aperture for fluid, saidaperture being located adjacent said axis and having a radial lengthsmall relative to the aforesaid radial displacement, fluid in saidchamber being responsive to external motivation to produce rotationalvelocity of said fluid about said axis, a rotatable member locateddownstream of said aperture and in fluid flow communication therewith,means for determining the rate of rotation of said rotatable member, andmeans for developing signals indicative of the velocity and direction ofrotation of said rotatable member.

3. The combination according to claim 2 wherein said means fordeveloping generates an electrical signal.

4. The combination according to claim 2 wherein said means fordeveloping is a rotary electrical generator.

5. The combination according to claim 3 further comprising means forinducing rotation of said fluid in said chamber.

6. In a vortex system, a cylindrical chamber of relatively large radius,means for supplying fluid irrotationally to said chamber, fluid in saidchamber being responsive to external motivation to produce rotationalvelocity of said fluid about said axis, said chamber having at least oneaxial egress port having a radial length small relative to the radius ofsaid chamber, said chamber having only fluid between said large radiusand a region defined by the radius of said egress port, means fordeveloping an electrical signal which is a function of the rate ofrotation of said fluid in a region of said chamber defined generally bysaid egress port, and wherein said means for developing is locatedwholly downstream of said egress port.

7. The combination according to claim 6 wherein said means fordeveloping includes a rotary electrical generator.

8. In a vortex system, a cylindrical chamber of relatively large radius,means for supplying fluid irrotationally to said chamber, fluid in saidchamber being responsive to external motivation to produce rotationalvelocity of said fluid about said axis, said chamber having at least oneaxial egress port having a radial length small relative to the radius ofsaid chamber, said chamber having only fluid between said large radiusand a region defined by the radius of said egress port, means fordeveloping an electrical signal which is a function of the rate ofrotation of said fluid in a region of said chamber defined generally bysaid egress port, wherein said means for developing is locateddownstream of said egress port, and further comprising a passageconnected in flow communication with said egress port, an enlargedregion formed in said passage, said means for developing including arotatable wheel located in said enlarged region.

9. In a fluid vortex device having a vortex chamber, said vortex chamberhaving an axis, fluid in said chamber being responsive to externalmotivation to produce a rotational velocity of said fluid about saidaxis, means for su-pplying said fluid to said chamber with substantiallyno rotational velocity, relative to said chamber about said axis and ata relatively large radius of said chamber, fluid outlet means locatedaxially of said chamber and including egress orifice means having aradius smaller than said relatively large radius by a large factor, andsensing means being responsive substantially only to said rotationalvelocity of said fluid in said chamber about said axis in terms of afunction of fluid and flow parameters, said sensing means being locatedwholly downstream of said egress orifice and including means forproviding an electrical signal representative substantially only of saidrotational velocity of said fluid wholly downstream of said chamberabout said axis.

10. The combination according to claim 9 wherein said sensing meanscomprises a phyiscal structure located in the flow of said fluid Whollydownstream of said egress orifice, said physical structure being movablein response to flow of said fluid about said axis of said chamber andmeans for producing an electrical signal which is a function of movementof said structure in response to flow of said fluid about said axis.

11. The combination according to claim 10 further comprising a fluidflow passage in flow communication with and coaxial of said egressorifice, said physical structure being located wholly in said fluid flowpassage.

12. In a fluid vortex device having a vortex chamber, said vortexchamber having an axis, fluid in said chamber being responsive toexternal motivation to produce a rotational velocity of said fluid aboutsaid axis, means for supplying said fluid to said chamber withsubstantially no rotational velocity, relative to said chamber aboutsaid axis and at a relatively large radius of said chamber, fluid outletmeans located axially of said chamber and including egress orifice meanshaving a radius smaller than said relatively large radius by a largefactor, and sensing means being responsive substantially only to saidrotational velocity of said fluid in said chamber about said axis interms of a function of fluid and flow parameters, said sensing meansincluding means for providing an electrical signal representativesubstantially only of said rotational velocity of said fluid in saidchamber about said axis, wherein said sensing means comprises a physicalstructure located in the flow of said fluid downstream of said egressorifice, said physical structure being movable in response to flow ofsaid fluid about said axis of said chamher and means for producing anelectrical signal which is a function of movement of said structure inresponse to flow of said fluid about said axis, and wherein saidphysical structure member is responsive to sense and amplitude ofrotational velocity of said fluid.

13. In a fluid vortex device having a vortex chamber, said vortexchamber having an axis, fluid in said chamber being responsive toexternal motivation to produce a rota tional velocity of said fluidabout said axis, means for supplying said fluid to said chamber withsubstantially no rotational velocity relative to said chamber about saidaxis and at a relatively large radius of said chamber, fluid outletmeans located axially of said chamber and including egress orifice meanshaving a radius smaller than said relatively large radius by a largerfactor, and sensing means responsive only to a rotational velocity ofsaid fluid in said chamber about said axis, said sensing means beingresponsive only to said rotational velocity of said fluid in saidchamber about said axis in terms of a function of fluid and flowparameters, wherein is included at least one source of tangentialcontrol fluid flow into said chamber from externally of said chamber,said at least one source being arranged to induce rotational motion ofsaid fluid in said chamber and constituting at least in part saidexternal motivation, said sensing means including means for generatingan electrical signal representative substantially only of saidrotational velocity of said fluid in said chamber.

14. The combination according to claim 13 wherein said sensing meanscomprises a physical structure located in the flow of said fluiddownstream of said egress orifice, said physical structure being movablein response to flow of said fluid about said axis of said chamber andmeans for producing an electrical signal which is a function of movementof said structure in response to flow of said fluid about said axis.

15. In a fluid vortex device having a vortex chamber, said vortexchamber having an axis, fluid in said chamber being responsive toexternal motivation to produce a rotational velocity of said fluid aboutsaid axis, means for supplying said fluid to said chamber withsubstantially no rotational velocity relative to said chamber about saidaxis and at a relatively large radius of said chamber, fluid outletmeans located axially of said chamber and including egress orifice meanshaving a radius smaller than said relatively large radius by a largefactor, and sensing means being responsive substantially only to saidrotational velocity of said fluid in said chamber about said axis interms of a function of fluid and flow parameters, said sensing meansincluding means for providing a signal representative substantially onlyof said rotational velocity of said fluid in said chamber about saidaxis, said vortex chamber having an end wall member lying in a planeperpendicular to said axis of said chamber, and wherein said means forsupplying said fluid includes means for supplying fluid directly intosaid chamber through the plane of said wall about the outer peripherythereof so that said fluid flows into said chamber in a path parallel tosaid axis.

16. In a fluid vortex device having a vortex chamber, said vortexchamber having an axis, fluid in said chamber being responsive toexternal motivation to produce a rotational velocity of said fluid aboutsaid axis, means for supplying said fluid to said chamber withsubstantially no rotational velocity relative to said chamber about saidaxis and at a relatively large radius of said chamber, fluid outletmeans located axially of said chamber and including egress orifice meanshaving a radius smaller than said relatively large radius by a largerfactor, said fluid outlet means having a passage extending from saidegress orifice and through which is adapted to flow substantially alongthe axis of said passage; and sensing means responsive substantiallyonly to said rotational velocity of said fluid in said chamber aboutsaid axis in terms of a function of fluid and flow parameters, saidsensing means including a blade element, said blade element beingpositioned wholly within said passage substantially parallel to the axisof said passage; and means operable to produce a signal indicative ofthe pressure differential across said blade element as a result of therotational velocity of said fluid flow relative to the axis of saidpassage.

References Cited UNITED STATES PATENTS 1 6 6/1957 Vonnegut 73194 5/1959Vonnegut 73-204 9/1959 Knauth 73229 11/1962 Dowdell 73-194 1/1965 Karlbyet a1. 73-231 FOREIGN PATENTS 6/ 1906 Germany.

RICHARD C. QUEISSER, Primary Examiner.

EDWARD D. GILHOOLY, Assistant Examiner.

US. Cl. X.R.

